Fluid flow mechanism



6 Sheets-Sheet l yov. 18, 194,1. Rv. s. SMITH "FLUID FLow MECHANISM 'Filed Nv. 2e, 1957 MMV Nw. 1s, 1941. R, s.. SMWH' 2,263,145

FLUID `FLOW MECHANISM Filed Nov. 26, 1937 6 Sheets-Sheva?, 2

Nw. 1s, 1941. y R. s. SMITH 2,263,145

FLUD FLOW MECHANI SM Filed Nov. 26, A193'? l 6 Sheets-Sheet 3 l y n Nov. 18, 1941., i R. s.vsMl'rH v I 2,263,145

FLUID FLOW MEGHANISM Filed Nov. 26, 1937 6 Sheets-Sheet 4 t/Qffarlzey.

Nov. 18,1941.

R. S. SMITH FLUID FLOW MCHANISM Filed Nov. 26, 1957 6 Sheets-Sheet 5 www@ fior/ay Nov. 1s, 1941. R s. SMITH f 2,263,145

VFLUID FLOW MECHANISM Filed Nov. 26, 1957 e 'sheets-sheet e flaring Patented Nov. 18, 1941 FLUID FLOW MECHAN ISM Reuben Stanley Smith, Altadena, Calif., assignor to Smith Meter Company, a corporation of California Application November 26, 1937, Serial No. 176,573

14 claims.

This invention relates generally to fluid flow mechanisms for use in measuring the volumetric flow of liquids, and is Vmore particularly concerned with metering devices of the rotary type.

It is the general object of the invention to provide a meter which operates with great accuracy, whether used for relatively heavy `and stable liquids or for highly volatile liquids such las gasoline.

The meter is of the general type fully described in my copending application, Serial No. 748,342-Fluid flow mechanism, led October 15, 1934, wherein the general features an-d many advantages are quite fully explained. It will be unnecessary to repeat them here. However, in the invention of the instant application, there are embodied a number of features giving advantage over the structures illustrated in said copending application.

For instance, in said copending application the inlet and outlet ports are arranged in the peripheral Wall of the meter housing or casing. This porting of the Wall naturally weakens it to a considerable extent and renders it subject to casting and pressure distortions, thus calling for special reinforcing expedients` which add to the Weight and complexity of the housing casting.

In contra-distinction to this, I here arrange the inlet and outlet ports'in the base vand cover, .y

respectively, of the housing, leaving the annular wall entirely unported and therefore with its strength undiminished. 'I'he 110W of the liquid from base-port to the now channel and from the ow channel to cover port, is spiraled, a single spiral partition serving to separate the ports'. Accordingly, the two ports Would, if vertically projected, overlap one another, and thus, to'- gether, they require the minimum of angularlymeasured space.

The top and. bottom porting has other advantages; for instance, it allows for the provision of a strainer or lter in the base casting-and a short-coupled faucet attachment for theoutlet port of the cover-thus compacting the assembly to an extent which enables it'to be tted within the cramped quarters which are so often allotted to devices of this type; and it allows the iloating off of relatively light foreign matter which may nd its Way into the meter in spite of the screen-while it adapts itself to the provision in the base of means whereby heavier foreign matter may be disposed of expeditiously.

The strainer is readily accessible forwcleaning and is so made up that while it will allow-free passage of liquid, it effectively traps most foreignmatter without linting up.

Other objects and features of novelty will be made apparent in the following detailed description.

Fig. 1 is a medial sectional view taken through a device embodying my invention, the sectionv through the cap of the air eliminator being taken on the line I--I of Fig. 12;

Fig. 2 is a reduced-scale plan view of Fig. 1;

Fig. 3 is a section on line 3--3 of Fig. 1, but showing the rotor as having been rotated to bring the blades into different positions;

Fig. 4 is a fragmentary section on line 4 4 of Fig. 3;

Fig. 5 is a section on line 5--5 of Fig. 1; Fig. 6 is a section on line 6 6 of Fig. 5;

Fig. 7 is a section on line 'I-1 of Fig. 6;

Fig. '7a is an end elevation of Fig. 7;

Fig. 8 is a perspective of the -abutment block; Fig. 9 is an inverted perspective of one of the rotor blade-units;

Fig. `10 is a fragmentary bottom plan view of Fig. l as viewed from the position of line IO-ID of that figure;

Fig. 11 1s a section on une 1| of Fig. 1o;

Fig. 12 is a plan view of the air eliminatorl with the head-cap removed;

Fig. 13 is a section on line I3--I3 of Fig.1;

Fig. 14 is a fragmentary-sectionfon line I4-I4 of Fig. 1; and

Fig. 15 is a fragmentary elevation of the interior of the housing wall as viewed from the position of arrow I5 in Fig. 3.

The meter, proper, is indicated generally at I0, While the air-eliminator and ilow `control is indicated at II, but I will rst describe the meter,` proper, and its operation Without'reference to the eliminator. p

The meter housing is generally indicated at I2 and includes an annular body member or barrel I3 `and end-closures or cover and base I4 and I5, respectively. Barrel or annulus I3 is flanged at I6 and I1, the flanges being bolted at I8 and I9 to cover flange 2|] and base flange 2|, respectively. IThe annulus flanges are recessed at 22 to take compressible gaskets 23.

Y It is important that the opposed faces 24 and 25 of closures I4 and I5 be maintained in accurate, vertically spaced relation, and of course, the joints between barrel and closures must be fluidtight. Accordingly, the several flanges are, throughout the major portions of their overlapping extent, firmly held4 in metal-to-metal contactto preserve this accurate spacing, while g-askets 23 are sufiiciently compressible to allow this condition to prevail and yet provide a fluid-tight joint. Grooves 28 in the annulus flanges provide clearances to accommodate any excess packing which may be squeezed out from grooves 22.

Base I has a diametrically extending through-passageway or screen chamber 21, the inlet end 28 thereof having an internal, annular flange 29 to receive and center ferrule 38 of strainer or screen-assembly 3|. Inlet 28 serves as the inlet to the meter, proper. This assembly is bodily withdrawable from and insertible in chamber 21 through open end 32. It includes a rectangular end cap 33 with hand-hold 34,

which is adapted to be detachably held to base I5 by bolts 35 (Fig. 7a) for closing the otherwise open end of the screen chamber, a gasket G being interposed between the cap and the opposed face of the base-casting. A cylindrical screen 36, made up of an inner sleeve 31 of relatively fine-mesh wire and outer sleeve 38 of relatively coarse-mesh wire, is solderedv at its opposite ends to ferrule 30 and disk 39, while it is centrally soldered to spider 48. Screw 4I extends through the spider and disk into cap 33, holding the strainer elements in assembly with end-cap 34, gasket G preferably being held clamped by screw 4|. between the inner face of the cap and the ends of the strainer sleeves and disk 39.

Fluid entering the ferrule-end of strainer 3|, is filtered or screened as it passes radially outward through sleeves 31 and 38 into the annular space 42 thereabout. It will be seen that the entire strainer assembly may be bodily removed for cleaning by merely removing bolts 35 and pulling on hand-hold 34.

Opening upwardly from space 42 is inlet passageway 43 (Figs. 1 and 4), the defining walls 44 and 45 giving this passageway an outward are. T he passageway terminates in inlet port 46 which is arcuately elongated, as viewed in Figs. 3 and 5, and opens to flow channel F.

Extending parallel to screen chamber 21 but at opposite sides thereof are two sump cavities 41 and 48 (Figs. 4, 6 and '7), these cavities terminating short of one end of theV base-casting as at 49; The outer ends of the cavities are closed by cap 33, though if desired, they may register with recesses 50 in that end-cap, gasket G being perforated at 5| to put the recesses and cavities into communication.

A sump passageway 52 extends from port` 53 in base-face 25 to cavity 48, so relatively heavy foreign matter within the ow chamber F (which will later be more particularly defined but which,

at this time, may be said to be defined at its bottom by face 25) may be swept into port 53 by the action of the rotor-blades (later to be designated) whence they fall through passage 52 into collection or settling cavity 48.

It will be seen that the portion, of the base casting at 54 forms a partition between ports 45 and 53.

The top of the base-casting is centrally depressed at 55 (Figs. 1, 5 and 6) below the annular face 25. Leading from this depression to cavity 41 is passageway 59, whereby relatively heavy foreign matter dropping into the depression from the rotor above, may be washed into passageway 53 and thence drop into settling or collection cavity 41.

It will be seen that when end cap 33. is removed, the foreign matter collected within cavities 41 and 48 may be quickly and easily flushed out.

Cover casting I4 has-p rovided in its face 2.4

an arcuately-elongated outlet port 58 which opens through outlet passageway 59 into chamber 68 of integral valve or faucet housing 6I (Figs. 1 and 4), wall 59 of passageway 59 ilaring away from the opposite wall 59". It will be seen that ports 4B and 58 have portions which, viewed in plan, overlap one another (the barrier separating the ports will be later described) thus giving the benefit of relatively long ports without appreciably reducing the useful angular extent of the flow passage.

Rising from the center of depression 55 is hub or post 62 having a vertically extending bore 63, a uniformly accelerated motion cam 64 being fixed' at 65 to an elevated portion 68 of the post at one side of bore 63. Cam 64 has an over-size opening 81 to take vertical cam shaft 68, but it overlies the bore sufficiently to serve as a detachable keeper for retaining certain underlying bearing-parts (to be described later) when the shaft is not in place.

Press-fitted within bore 63 is a rust-proof bushing 891 within which a thirnble or block 10 is mounted for Vertical, adjustable sliding movement. Slide block 18 is cylindrical, having an end-wall 1I taking adjustment screw 12, and a sleeve portion 13. Keyway 14, milled in the side of the thimble, takes key-pin 15 carried by hub 62, the slide block thus being keyed against rotational movement. Hole 16 in the sleeve-wall, communicates with hub-passageway 11 in the various positions of vertical adjustment of the slide block, this provision allowing foreign matter within the sleeve-bore to be flushed into depression 55, whence it is disposed of as previously described.

Adjustment screw 12 extends through the unthreaded base-bore 18, its head 19 engaging shoulder 88 at the end of counter-bore 8| to limit the upward movement of slide block 19 as urged by compression spring 83. Preferably, the end of block 18 is split as at 84 after the tapping operation, and the free portion 85 is then distorted axially so that when screw 12 is inserted, the springiness of said portion has the effect of a lock-washer which will not positively prevent relative movement of block and screw but will impose enough resistance thereto to hold the block in adjusted position against the loosening effects of vibration and the like. Block 18 supports radial bearing 86 and thrust bearing 81, both being of the anti-friction type and carrying and taking pin 88 which is pressfitted in bore 89 of shaft 68, and thus, in effect,

' is a part of that shaft.

This shaft 68'may be considered a part of the rotor assembly generally indicated at R and provides means for supporting that assembly in proper relationship to the meter housing. The upper end of the shaft is bored at 90' to take the press-fitted, elongated hub 9|)v of pinion 9|. Press-fitted in the bore 92A of the pinion isla pin 93" which has bearing within a bushing 94, the latter being press-fitted into the bore of cover casting I4'y the pin being slidable vertically within the bearing bushing to-accommodate vertical adjusting movement of the shaft. Due to the fact that bearing assemblies 86 and 81 are about mid-way of the vertical length of rotor assembly R, they are capable of taking the greater part of any radial bearing force, and therefore it is unessential that the upper bearing bushing 94 be of the Vanti-friction type.

TheY pinion 9| meshes with gear 96 carried on shaft 91' which extends verticallyy through cover ,I4 to compartment 98. Shaft9`| ispack'ed-off by jthe packing assembly indicatedggenerally ,at

99, the details ofwhich need not be` entered into here.i The upper end of the shaft carries a gear which, through gear train generally designated at |0| drives pinion |02 on counter-shaft |03. This counter-shaft is adapted `to actuate the counter or register mechanism generally indicated at |04, which makes up no part of the present invention,

As has lbeen said, shaft 68 makes up part of the rotorN assemblyor unit R. 'Ihe assembly is further made up of an annular body member or carrier |having a web |06 extending across thev topvthereof, theweb being ribbed at I06a and supporting a hub |0'| within the bore |08, of which, is press-fittedA shaft 68, it following ythat rotation of body |05 acts, through shaft 68 and the gear train previously described, to actuate counter |04.V

An in-turned annular ilange |09V (Fig. 11) is provided at the lower end of body |05, while the annular wall I I0 has four radial slots III, equally spaced apart and extending from top to bottorn` of the annulus. Flange |09 and web |06 have slots ||2 and ||3, respectively, each of which register with the opposite ends of slots I I I, though slots ||2 and I3 may be wider than slots I to provide for greater blade clearance at these points.

There are provided two blade units indicated generally at I I4 and II5, each unit embodying a pair of blades ||6 connected by yoke ||1 (Fig. Sil-wherein the blade unit is inverted, top for bottom), the lower ends of the blades being extending inwardly or toward each other as at ||6. The two blade units are individually fashioned so the yokes I Il thereof are spaced apart vertically, as clearly shown in Fig. 1, but both yokes encircle shaft 68 as clearly shown in Fig. 3. Each blade unit supports, by pin-s ||8, a pair of dia.- metrically opposite cam rollers ||9, the rollers being conned by their press-fitted bushings within the slots I2I. The rollers of both blade units are adapted to engage cam 64, as illustrated. Blade unit I I5 differs from the showing of Fig. 9 only in that its yoke is most distantly spaced from ends ||6 and the yoke arms are spread sumciently at |I5 to accommodate the downward extension of hub |0' Y `Applied to annular shoulder |24 on the undersideof ilange `|09 is a. ring |25, attachment be` tween `flange and ring being made by screws |26. It will be noted shoulder I 24 is slightly below the under-surface |23 of flange |09. The ring thus underlies a portion of the extent of each slot ||2, and screws |26 plus pins |21 (the latter extending through ring and flange) are arranged at opposite sides of the annulus and ilange slots, serving to hold the slotted end of the annulus from spreading and thus denitely and permanently establishing the widths of sai-d slots so that predetermined clearancesI between the slot-walls and blades ||6 are exactly maintained.

Blades i6 slide through slots III, I|2 and II3, and are supported for shuttling movement by hardened polished steel blocks |28 (Figs. 10 and 11) which are held to the under-surface |23 of ange |09 and in a'position to bridge slots ||2 by clamps |29, the latter being held to ring by .screws |26 and havingangular lugs |30 engaging the bottoms'ofsockets |3I. These blocks maintain the lower edges of blades ||6 in exact horizontal alignment with the under-surface |23 of flange |09 and inspaced relation to theupper surface of ring |25. 'Adjustment screw I2 is adjusted So that the' common horizontal plane of the undersurface |23 of the flange and the bottoms of the blades lies spaced slightly abovehousing face^25, so that slight clearance L is maintained between the faces in that plane and the face 25. This clearance L, .as well as other clearances-are shown of exaggerated extent in the drawings, but actually represent only a few thousandths of an inch. i

Spring 83 maintains the rotor body in a position of elevation to preserve this clearance, while the head 'I9 of screw I2 in its engagement with shoulder limits the upward movement of the rotor and preserves the clearance M between face 24 of cover |4, on the one hand, and the upper` edges of the blades and the upper edge of annulus |05 o n the other hand, said edges being flush. The clearance M is substantially equal in extent of that of clearance L.

, Screw 'I9 is reached for adjustment by removingl the strainer assembly 3| and housing plug |35, whereupon a screw driver may be inserted through -the plug-hole and into engagement with the screw.

It will be noted that the entire rotor unit R is resiliently supported on spring 83, so in case of sudden downward jar, the spring serves to absorb the initial shock and the bearings 86 and 81 are relieved therefrom. If the shock be severe, the rotor may momentarily contact face 25, but even should this happen, the shock is taken evenly over the entire under-face of the rotor-the possible load transmitted to the bearings being at all times limited to the spring pressure which is well within their capacity to withstand.

Now referring to Fig. 3, it willv be noted that the annular flow channel F is defined by the inner wall of casing I3 and the periphery of rotorannulus IIIl. Opening to this channel are inlet port.46 and outlet port 58, the flow through channelF being in a clockwise direction, as Viewed in this figure.

Interposed in flow channel Fand, in effect, betweenports 46 and 58, is provided a barrier block |40 (Figs. l, 3, 4 and 8), which may broadly be considered a part of casing barrel I3. It consists of anarcuate plate portion |4| held in annularly spaced relation to casing I3 by partition |42 and stream-lined lugs |43, -attachment to the casing being made by bolt |44. Preferably, the. machined casing-surfaces against which partition |42 and lugs are drawn by bolt |44, are provided on projections |45 and |46, respectively, which extend integrally and inwardly from casing I3. A

Partition |42 may be considered as a rib on plate-portion |4| and extending diagonally or spirally from bottom to top of flow channel F, for it rests on portion 54 of base-face 25 and extends to cover face 24 at a point vertically offset from portion 54.

The lower end of partition wall |41 registers with one endof inlet port 46 and then curves in a relatively wide sweep toward face 24. The upper end of the opposite partition wall |48 extends from one end of port 53 and then curves in a relatively wide sweep to one end of port 58. These walls, in their association with walls 45 and 59', dene easy, smoothly curving passageways which contribute to the even and uninterrupted iow of liquid through the meter. It will be seen that the liquid, in passing from chamber 42 to the now channel and from the flow channel to outlet chamber` 60, may be considered as following a spiral path. It will be seen that the center of outlet chamber 60 is in vertical alignment with inlet chamber 21 (Fig, 4)

The outer face of plate-portion |4l of block |40, is recessed from top to bottom to provide a clearance passageway |50 between the rotor and block. This recession leaves vertically extending lugs and |52 near the ends of the block, which. lugs are spaced apart slightly less than 90 and establish diminished clearance passageways |53, which, taken together with passageway |50, may be considered a return or corrective passageway, the significance of which is fully pointed out in said copending application.

Diametrically opposite block |40, the inside of housing wall I3 is accurately machined at |54 throughout an angular extent of at least more than 90, this portion of the wall and the opposite wall of the rotor annulus defining the sides of measuring chamber S which is, of course, a part of flow channel F. The measuring' chamber is defined at top and bottom by faces 24 and 25 and at its ends by any two adjacent rotor blades when both are within the limits of face |54. The dimensions of the measuringl chamber are such that its volumetric capacity will have a known value to which counter |04 maybe accommodated to register in any chosen unit of measure.

Cam 64 is so located that, upon rotation of the rotor, a given blade is projected to its farthest extent just before it reaches the measuring chamber, the opposite blade of that unit simultaneously reaching its position of full retraction (preferably a little below the peripheral face of the rotor to insure ample clearance with respect to block-lugs |5|, |52) just prior to reaching lug 5|. The cam rollers ||8 of that unit then ride over dwells |55 and |56 which maintain the blades in their respective positions of full projection and retraction until just after they leave the measuring chamber and lug |52, respectively. The path of a given blade during one revolution of the rotor is indicated in dotted lines H in Fig. 3.

As the fluid ows through inlet 46, it is guided by the smoothlyv curving walls of the inlet passageway intov flowv channel F. In its passage through the flow channel, the uid acts against such rotor blades as are in its path in a manner to cause rotor rotation which, in turn, shuttles the blades in the manner described. The fiuid then is guided b'y the smoothly curving walls of the outlet passageway and is iinally'delivered through the faucet-valve, to be described;

The mounting and association of the various parts of the rotor render it capable of smooth and easy rotation under the slightest of impulses. Accordingly, but little resistance is offered to the flow of fluid through the meter and, since the blades are being bodily carried in the direction of fluid-flow and at practically the same velocity thereas, said blades do not, by virtue of radial movement through the fluid-stream to the projecting positions, appreciably retard the passages of the fluid from the inlet to the measuring chamber.

Centrifugal force tends to hold each blade successively outward as itv is extended beyondits central position, thus holding an associated cam roller firmly in Contact with the small-radius dwell |56 during movement of the cam blade through the measuring chamber. This insures that the blade will normally clear measuring chamber wall |54 by a predetermined extent, as at L (Fig. 1), eliminating frictional drag` and insuring predetermined slippage past the blades, all of which contributes to the securement of accurate metering results, as more particularly pointed out in said co-pending application,

In spite of strainer 3|, extraneous matter may nd its way into the ow channel and, of course, there' may be present metal chips 0r core-sand remaining within the meter after' assembly, or there may be metal particles which become detached during meter operation. It has been said before that the lighter particles are floated out through chamber 60, while the heavier particles within the flow channel drop to the bottom and are swept by the fluid ahead of the blades to port 53,- where they drop to sump cavity 48. It will be noted that port 53 extends substantially across the full width of the flow channel and is located at' a point beyond the shuttling range of the rotor blades (see Fig. 3, where the dotted line H indicates said range). Likewise it' will be seen the heavier particles within the rotor unit drop to depression 55, whence they finally pass through passageway 56 into sump-cavity 41.

In order to rid the vertical edges of the blades of sand or other foreign matter which may have a tendency to cling thereto, I provide a vertical series of recesses |60 (Figs. 3 and 15) in the inner wall of casing |3 at the point where the blades first reach their position of full extension. The recesses are vertically defined by diagonal ribs' |6I, and it is found that the resulting diagonal or spiral formation of the recesses gives the fiuidv a sweeping eifect over the edges of the blades which effectively dislodges extraneous matter therefrom. It will be seen that the positioning of the recesses insures that the ext-raneous matter is cleared away before it can be trapped between the blade-edges and the machined casing-wall of the measuring chamber, and thus scoring and drag are prevented. In the yevent such wear develops in the cam rollers or theirl mountings as t0 allow blades ||6 to be moved by centrifugal force into contact with Wall |54, the slight blow of the initial impact is taken on the spaced ribs |6|, and the extraneous4 matter on the blade-edges between ribs is projected into the recesses where it is washed away by the fluid spiraling therethrough, inste'iidof being driven against or into the casing- Wa l.

I have indicated generally at |62 a valve or faucet for controlling the outlet of the meter. The details of the valve are set forth in my copending application entitled Fluid meter and faucet valve therefor, filed January 19, 1938, Serial No. 185,682; but it will suffice for present purposes to statev that it includes a disk-stopper |63carried on an arm |64 extended from rock shaft |65. Shaft |65 is journalled in housing |66, the latter being applied to housing 6| by bolts |61 (Fig. 2). In closed condition, disk |63 engages seat |68; while rotation of shaft |65 is effective to move disk |63 to the open position indicated in dotted lines.` Housing |66 has an outlet neck |69to which attachment of the delivery pipe or the line (not shown) is made. Stopper |63 is operated to and from closed position by handle i65a on shaft |65 (Figs. 1 and 2).

The air eliminator and flow regulator includes a cylindrical barrel or casing |10 extending vertically from the integral and horizontally extending casing or pipe |1|, the bore of floatchamber |12 of casing |10 opening at |13 to horizontal bore |14. One end of pipe |1| has an attachment flangeY |1'|' applied by bolts |15 to4 flange 29 at the side of meter base I5, whereby eliminator bore |14 is put into communication with meter-inlet 28. The opposite end of pipe |1| has a fitting |16 applied to its attachment flange |16 by bolts |11, the inlet or stand-pipe |18 being secured to fitting |16' by elbow |19.

' Within pipe bore |14 at the right (Fig. 1) of float-chamber opening |13, is a flow-control valve |80 (Fig. 13). This valve, of the butterfly type, is circular, as viewed axially of the pipe, and is of a diameter to t bore |14. It includes a horizontal hub |8| taking shaft |82 whereby the valve is mounted for oscillatory movement to and from closed position. Shaft |82 has bearing in bores |83 in the pipe-wall, while plugs |84 hold the shaft against end-wise displacement, one, at least, of the plugs being removed to allow assembly or disassembly of the valve and its shaft within bore |14,

Disk |80 may be considered as made up oi' two blades |85 and |86, said blades lying at opposite sides of the vertical axial plane of shaft |82. In closed position each blade has a diagonally extending inner portion |81, while the outer portion |88 extends substantially vertically, the square-cut-ends |89 of the blades engaging pipe |1| as a positive stop to prevent counter-clockwise movement from the full-line position of Fig. l and thus establishing the closed position of the valve.

By reason of' this offset arrangement of the valve blades, I overcome the depression effect usual to most valves of this type, which acts (as such valves are initially opened and by reason of the rapid fluid-flow past the end of one of the angularly disposed blades)4 in a manner tending to reclosethevalve and thus materially to interfere with the nice balance necessary to successful operation of a float-operated butterfly valve throughout its various positions of adjustment.

Adapted to reciprocate vertically within float chamber |12 is a float |90 here shown as made up of a cylindric metal shell I9| whose ends are closed at |92 and |93. From top |92 extends a vertical leg |94 of channel cross-section (Fig. l2) which is privotally connected at`|95 to arm |96 of bell crank |91. Crank I 91 extends through a slot |98 in plate |99 which is an integral part of cap 290. Cap 200 is bolted' at 20|` to ange 202 of casing |10, and may be considered as making upa portion of the top closure or head generallyindicated at'203. Head 203 is completed by cap 204, secured to cap 200 by bolts 294 (Fig. 2). Gaskets 205. and 206 are interposed between cap 200 and casing at one side and caps 200 and 204, at the other side.

Bell crank |91-is pivotally supported by a pin 201 (Fig. 12) supported from plate |99 by boss 299. Also extending from plate |99 is an elongated boss 209 which has a vertical bore 2|0 extending from its upper machined face 2|| to horizontal bore `2|2 which extends horizontally to boss 2|3 at the outer edge of the cap and which provides a threaded socket 2|4 for the reception of by-pass pipe 2|5.

Sliding on Aface 2 of boss 299, is a slide valve 2|0, which may be conveniently made up `oi a disk of such material as Catalan Disk 2lb` has a central socket 2|1 adapted to take the lower end of pin 2|8 which is carried by arm 2|9 pivotally connected at 220 to crank |91. Pivot pin 220 is extended to receive a coiled torsion spring 22|, the looped extremities of which engage cotter key 222 carried by the pivot pin, and transverse pin 223 carried by arm 2|9, respectively. The effect of this spring is to tend to rotate arm 2|9 in a counter-clockwise direction (as viewed in Fig. 1) so as always to pressurally engage disk 2|6 with face 2| said face and disk being lapped to insure full-area contact. Spring 22| thus acts to hold disk 2|6 flat against face 2|| irrespective of the bodily left or right sliding movement imposed on that disk by virtue of bell crank movement, the t between pin 2|8 and socket 2I1 being suifciently free to allow the slight rocking movement of the pin during such bell crank movement. The disk is also capable of rotation about the pin-thus giving it self-cleaning and self-lapping characteristics.

The upper end of pin 2|8 is extended into close proximity with the underface of cover 204, to prevent, during shipment or rough handling, la sufficient extent of clockwise movement of arm 2|9 as to accidentally dislodge pin 2||3 from socket 2|1.

It will appear that when float |90 risesV from the full line of Figl 1 to the dotted line position, bell crank |91 will be rotated clockwise, thereby bodily drawing arm 2|9 and disk 2|6 to the right and causing said disk to close olf passageway 2|0.

Extending downwardly from float |90 is leg'224 of channel cross-section (Fig. 14) which is pivotally connected at 225 to crank arm 226 extending from and integral with valve |80. It will be seen that downward movement of the float is limited to the extent shown in Fig. 1 by reason of the contact of valve edge |89 with pipe |1|. Likewise', it will be seen that the float is supported solely by its connection with valve arm 226 and with bell crank |96, there thus being no necessity for, providing'guides, Vor the like, common to most oat valves, which are very likely to stick or bind the floats. Of course, in its vertical travel, the iioat will have a component of horizontal bodily movement but this is in no way disadvantageous since ample annular clearance is left between the-float and the wall of the float chamber |12.

In the normal condition of the entire system and with faucet valve |92 closed, the meter will becompletely filled with fluid and the fluid'in chamber |10 will hold float |90 in its uppermost position (dotted lines in Fig. 1) wherein the airoutlet valve' generally indicated at V, made up of boss 209 andi disk 2|6, is closed, and regulator valve is in the open position indicated by dotted line. Air will be trapped in the air chamber A above the fluid in chamber |12, as well as in the valve `chamber B.

In this condition, valve |80 offers no appreciable resistance to the flow of uid through bore |14 and thence through the meter to outlet |69 when faucet |62 is opened. However, should there be air entrained in the incoming fluid, it will naturally seek to rise therethrough and, upon reaching a point below the float chamber will pass upwardly through the float chamber liquid and into air chamber A, thus being prevented from passing through the meter and causing a false reading to be given by counter |04.

As the air gathers within chamber A, it downwardly displaces the fluid within the float chamber and raises the air pressure within that chamber. This displacement of fluid causes the float to drop, thus shifting valve-disk 2|6 toward the left in Fig. 1. As the float drops, it tends to move valve |80 toward closed position and the valve, in its partly closed position, acts as a baille to more definitely direct the fluid with'itsentraned air into the oat chamber, to give that air a better and longer opportunity to rise to chamber A.

When the air Within the chamber has gathered to an extent sufficient to drop the float to a position Where air-valve V is opened, the air, under its built-up pressure, will flow through passageway 2|0 and 2|2 into by-pass tube 2|5, and by this action chamber A will be drained of air sufiiciently to allow fluid again to rise in the iloat chamber until valve V is again closed. So long as the incoming fluid contains entrained air, these intermittent air-releases will occur.

Broadly, by-pass pipe 2 I 5 may run to any point of delivery, but since it usually contains explosive vapors, it is preferred that it be led back into the line at a point beyond the measuring chamber of the meter. Accordingly, I have here shown pipe 2 I5 as being tapped back into faucet-chamber 60 at 2|5. This particular manner of bypassing the air has a further advantage, for when the control valve |80 is in partly closed position, the rush of fluid through neck |69 will tend to create depression about the outlet of the by-pass and thus aid in quickly and suddenly emptying chambers A and B of the excess air.

It will be noted that the elevation of outlet port |69 With reference to the ow channel F of the meter is such that When the fluid 'supply to which pipe |18 is connected becomes exhausted so that the level of such inlet fluid is depressed to a point substantially level to the outlet |69, as indicated by the dotted line Y, flow will cease but the meter flow channel Will have a sufficient volume of fluid trapped below this level to remain completely filled and thus exclude air from the meter channels and prevent drainage of the rotor chamber or other meter channels.

When the supply tank is refilled and additional fluid passes into the eliminator, the meter operation is resumed Without inaccuracies of measurement which might exist if air had been admitted to the meter channels.

While I have shown and described a preferred embodiment of my invention, it will be understood that various changes in design, structure and arrangement may be made Without departing from the spirit and scope of the appended claims.

I claim:

1. In a fluid ow mechanism, a casing embodying a vertically arranged barrel having a cylindrical bore and top and bottom covers fixed thereto, a rotor body concentrically mounted in the barrel bore for rotation therein, the rotor being annularly spaced from the barrel Wall, a barrier xed to the barrel and disposed in the annular space defined by the barrel and rotor body, the space extending continuously from end to end of the barrier comprising the flow channel and said covers defining the top and bottom of the flow channel, rotor blades mounted for shuttle movement transversely of the flow channel and for radial retraction as they individually pass said barrier during rotor-rotation, there being an inlet in said bottom cover opening to the channel at one side of the barrier, and there being an outlet in said top cover opening from the channel at the other side of the barrier, said inlet and outlet being substantially in vertical alinement.

2. In a fluid flow mechanism, a casing embodying a vertically arranged barrel having a cylindrical bore and top and bottom Vcovers fixed thereto, a rotor body concentrically mounted in the barrel bore for rotation therein, the rotor being annularly spaced from the barrel wall, a barrier fixed to the barrel and disposed in the annular space defined by the barrel and rotor body, the space extending continuously from end to end of the barrier comprising the ow channel and said covers defining the top and bottom of the ow channel, said barrier extending diagonally between covers, rotor blades mounted for shuttle movement transversely of the oW channel and for radial retraction as they individually pass said barrier during rotor-rotation, there being an inlet in said bottom cover opening to the channel -at one side of the barrier adjacent the lower end thereof, and there being an outlet in said top cover opening from the channel at the other side of the barrier adjacent the upper end thereof, said inlet and outlet being substantially in vertical alinement.

3, In a fluid flow mechanism, a casing embodying a vertically ararnged barrel having a cylindrical bore and top and bottom covers xed thereto, a rotor body concentrically mounted in the barrel bore for rotation therein, the rotor being annularly spaced from the barrel Wall, a barrier fixed to the barrel and disposed in the annular space dened by the barrel and rotor body, the space extending continuously from end to end of the barrier comprising the flow channel and said covers dening the top and. bottom of the flow channel, rotor blades mounted for shuttle movement transversely of the flow channel and for radial retraction as they individually pass said barrier during rotor-rotation, there being an inlet port in said bottom cover opening to the flow channel and an outlet port in said top cover opening from said flow channel, said ports being substantially in vertical alinement, said barrier extending diagonally from cover to cover and from a point adjacent one end of the inlet port to a point adjacent the opposite end of the outlet port.

4. In a iluid iloW mechanism, a casing embodying a vertically arranged barrel having a cylindrical bore and top and bottom covers fixed thereto, a rotor body concentrically mounted in the barrel bore for rotation therein, the rotor being annularly spaced from the barrel Wall, a barrier fixed to the barrel and disposed in the annular space defined by the barrel and rotor body, the space extending continuously from end to end of the barrier comprising the ilovv channel and said covers defining the top and bottom of the flow channel, rotor blades mounted for shuttle movement transversely of the flow channel and for radial retraction as they individually pass said barrier during rotor-rotation, there being an inlet port in said bottom cover and an outlet opening in said top cover, said ports being substantially in vertical alinement and opening to the flow channel at bottom and top, respectively, thereof; and said barrier embodying an arcuate plate-portion spaced annularly from the barrel Wall and a rib extending from cover to cover and from the arcuate portion to the barrel Wall, said rib also extending from one end of the inlet port to the opposite end of the outlet port.

5. In a iluid flow mechanism, a casing embodying a vertically arranged barrel and top and bottom covers therefor, a rotor body mounted for rotation about -a Vertical axis in the barrel bore, saidbarrel and rotor body dening the sides of a flow channel, rotor blades mounted for shuttle movement transversely of the floW channel, one side of the rotor body being positioned adjacent a portion of the casing to form a barrier defining the ends of the flow channel, there being inlet and outlet ports in the casing at opposite sides of and adjacent the barrier, the outlet port being in communication with the top `of the iiow channel and there being a settling cavity in the bottom cover and a port in the bottom-dening wall of the ilow channel at the outlet end thereof and adjacent the barrier, said last mentioned port opening downwardly to said settling cavity, s-aid port extending substantially across the full width of the ilow channel at a point beyond the shuttling range of the blades.

6. In a fluid flow mechanism, a casing embodying a vertically arranged barrel and top and bottom covers therefor, a rotor body mounted for rotation about a vertical axis in the barrel bore, said barrel and rotor body deiining the sides'of a flow channel, rotor blades mounted for shuttle movement transversely of the llow channel, one

side of the rotor body being positioned adjacent a portion of the casing to form a barrier dening the ends of the flow channel, there being inlet and outlet ports Vin the casing at opposite sides of the barrier, and there being a pair of f,

of the ow channel and'opening downwardly to one of the settling cavities, and there being an unrestricted port in said bottom'cover opening downwardlyy from a point beneath the rotor to the other settling cavity, a pair of clean-out openings,ione for each cavity, and a common detachable closure for ings. Y

7. In a fluid flow mechanism, a casing embodying a vertically arranged barrel having a cylindrical bore and top and bottom covers xed thereto, a rotor body concentrically mounted in the barrel bore for rotation therein, the rotor being annularly spaced from the barrel wall, a barrier fixed to the body and disposed in the annular space defined by the barrel fand rotor body, the space extending continuously from end.

stantially in vertical alinement and opening to i.'

the flow channel at bottom and top, respectively, thereof; and said barrier embodying an arcuate plate-portion spaced annularly from the barrel wall and a rib extending from cover to cover and from the arcuate portion to the barrel wall, said rib also extending diagonally upward from one side of the inlet port in the bottom cover to the opposite side of the outlet port in the top cover, the downwardly presented face of the rib lying vertically above the inlet port and curving smoothly toward the upper cover in the direction of uuid-flow from the inlet port to the ilow channel.

8. In a fluid flow mechanism, a casing embodying a vertically arranged barrel having a cylindrical bore and top and bottom covers xed thereto, a rotor body concentrically mounted in the barrel bore for rotation therein, the rotor being annularly spaced from the barrel wall, a barrier fixed to the body and disposed in the anboth said clean-out open-` lib nular space defined by the barrel and rotor body, the space extending continuously from end to end of the barrier comprising the flow channel and said covers dening the top and bottom of the ilow channel', rotor blades mounted for shuttle movement transversely of the flow channel and for radial retraction as they individually pass said barrier duringr rotor-rotation, there being an inlet port vin said bottom cover. and an outlet opening in said top cover, said ports being substantiallyin vertical alinement and opening to the`flow channel at bottom and top, respectively, thereof; and saidV barrier embodying an arcuate plate-portion spaced annularly from the barrel wall 'and a rib extending from cover to cover and from the arcuate portion to the barrel wall, said rib also extending diagonally upward from one side of the inlet port in the bottom cover to the opposite side of the outlet port in the .r top cover, the downwardly presented face of i being annularly spaced from the barrel wall, a

barrier xed to the body and disposed in the annular space defined by the barrel and rotor body, the space extending continuously from end to end of the barrier comprising the flow channel and said covers deiining the top and bottom of the ilow channel, rotor blades mounted for shuttle movement transversely of the flow channel and for radial retraction as they individually pass said barrier during rotor-rotation, there being an inlet port in said bottom cover and an outlet opening in said top cover, said ports being substantially in vertical alinement and opening to the ilow channel at bottom and top, respectively, thereof; and said barrier embodying an arcuate plate-portion spaced annularly from the barrel wall and a rib extending from cover to cover and from the arcuate portion to the barrel wall, said rib also extending diagonally upward from one side of the inlet port in the bottom cover to the oposite side of the outlet port in the top cover, the downwardly presented face of the rib lying vertically above the inlet port and curving smoothly toward the upper cover in the direction of fluid-flow from the inlet port to the ow channel, and the ilow channel where it extends horizontally opposite said face being substantially uninterrupted by barrier and casing structure.

l0. In a fluid flow mechanism, a casing embodying a vertically arranged barrel and top and bottom covers therefor, a rotor body mounted for rotation about a vertical axis in the barrel bore, said barrel and rotor body defining the sides of a liow channel, rotor blades mounted for movement transversely of the flow channel, one side of the rotor body being positioned adjacent a portion of the casing to form` a barrier dening the ends of the flow channel, there being a horizontally extending inlet passageway in the bottom cover and a port opening from said passageway into the flow channel adjacent one side of the barrier, and there being an outlet passageway through the casing from the flow channel adjacent the other side of the barrier, there being a settling cavity in said bottom cover at one side of ,the inlet passageway but isolated therefrom, and there being a port in the bottom cover opening from the flow channel `downward-ly into said settling cavity.

11. In a .fluid flow mechanism, a casing embodying a vertically arranged barrel and top and 'bottom covers therefor, a rotor body mounted for rotation about a vertical axis in the barrel bore, said barrel and rotor body dening the sides of a ow channel, rotor blades mounted for movement transversely of the ow channel, one vside of the rotor body being positioned adjacent a portion of the casing to form a barrier defining `the ends of the ow channel, there being a horizontally extending inlet passageway in the bottom cover and a port opening from said passageway into the flow channel adjacent one side of -the barrier, and there being an outlet passageway through the casing from the flow channel adjacent the other side of the barrier, there being a settling cavity in said bottom cover at one side of the inlet passageway but isolated therefrom, and there being a port in the bottom cover adjacent the other side of the barrier and opening from the flow channel downwardly into said settling cavity.

l2. In a iiuid flow mechanism, a casing embodying a vertically arranged barrel and top and bottom covers therefor, a rotor body mounted for rotation about a vertical axis in the barrel bore, said barrel and rotor body defining the sides of a flow channel, rotor blades mounted for movement transversely of the flow channel, one side of the rotor body being positioned adjacent a portion of the casing to form a barrier defining the ends of the flow channel, there being a horizontally extending inlet passageway in the bottom cover and a port opening from said passageway into the ow channel adjacent one side of the barrier, and there being an outlet passageway through the casing from the flow channel adjacent the other side of the barrier, there being a settling cavity in said bottom cover at one side of the inlet passageway but isolated therefrom, there being a port in the bottom cover opening from the flow channel downwardly into said settling cavity, there being a second settling cavity in the bottom cover at the other side of vsaid inlet passageway but isolated therefrom, and there being a second port in the bottom cover Vopening downwardly from a point beneath the rotor to said second cavity.

13. In a fluid ilow mechanism, a casing, a rotor body mounted for rotation about a vertical axis within the casing, said casing and rotor body dening the sides of a iiow channel, rotor blades carried by the body and mounted for radial shuttle movement transversely of 'the flow channel, one side of the rotor body being positioned adjacent a portion of the casing to form a barrier defining the ends of the ow channel, means for shuttling said blades, the blades individually initially reaching their position of full radial extension when they are opposed to a point on the casing which is spaced angularly from the barrier at the inlet side of the flow channel, and there being a substantially vertical series of recesses inthe casing wall approximately at said point, said recesses defining between them a substantially vertical series of ribs having faces which are substantially iiush with the flowchannel defining face of the casing.

14. In a fluid flow mechanism, a casing, a rotor body mounted for rotation about a vertical axis within the casing, said casing and rotor body dening the sides of a flow channel, rotor blades carried by the body and mounted for radial shuttle movement transversely Vof the ow channel, one side of the rotor body being positioned adjacent a portion of the casing to form a barrier dening the ends of the flow chanel, means for shuttling said blades, the blades individually initially reaching their position of full radial extension when they are opposed to a point on the casing which is spaced angularly from the barrier at the inlet side of the flow channel, and there being a substantially vertical series of diagonal recesses in the casing wall approximately at said point, said recesses defining between them a substantially vertical series of diagonal ribs having faces which are substantially flush with the now-channel defining face of the casing.

REUBEN STANLEY SMITH. 

